Rotary, turbine-type fluid coupling



1953 F. w. SEYBOLD ROTARY, TURBINE-TYPE FLUID COUPLING 2 Sheets-Sheet 1 Original Filed July 21, 1951 INVENTOR. FREDERICK w. SEYBOLD BY 57%,,

ATTORNEYS Nov. 10, 1953 Original Filed July 21, 1951 FIG-4 F. W. SEYBOLD ROTARY, TURBINE-TYPE FLUID COUPLING 2 Sheets-Sheet 2 INVENTOR.

FREDERICK *w. SEYBOL By(;; 4 I I 2M 5 ATTORNEYS Patented Nov. 10, 1953 UNITED STATES PATENT OFFICE Original application July 21, 1951, Serial No. 237,974, Divided and this application January 19, 1953, Serial No. 331,793 r 10 Claims. (01. 5 9 4 This invention relates to power transmitting devices, particularly to fluid coupling arrangements and combinations thereof with variable speed gearing.

Such transmissions as are referred to above are adapted for mounting between the power plant and the driven shaft of automotive verhicles such as passenger cars, trucks, and military tanks and for other power transmission ap-.- plications requiring variable speed output.

In particular, variable speed transmissions of this nature, namely, the combination of a fluid drive unit and geared drive unit arranged in series are becoming more or less standard equip! ment for passenger automobiles. Previous com-. binations of this nature however, have certain disadvantages in connection with either their construction, maintenance, or operation that render them somewhat less satisfactory than is to be desired.

One particular diificulty encountered with such transmissions is the extreme complexity of the control system and many transmissions in cur rent use have a plurality of brakes, friction clutches, jaw clutches and overrun clutches, at least some of which must be operated in over lapping or precisely consecutive relationship during speed changes of the transmission in order to obtain a reasonably smooth variation in the output speed of the transmission. The con trols necessary for accomplishing the shiftingof the various clutches and brakes are not only complicated and therefore expensive but are also subject to wear and failure and to becoming out of adj tm nt.

Whenever control systems of this nature be! ome out of dj st nt, and com n e to oper ate improperly for any reason whatsoever, a perc ptible shoc l take place in t e d e rain. betwe n th er p a t and he. output, shaft which is not only objectionable to the operator and passengers in the vehicle but is also dangerous in that severe loads imposed on th me! hem cal elemen s of he d ive tr n might caus failure thereof under certain conditions.

Having the foregoing in mind; it is a primary object of the present invention to provide the combination of a fluid coupling and a geared unit in a transmission characterized by extreme simplicity and smoothness of operation. I

A still further object is the provision of a, transmission of the nature referred to including a fluid coupling in which the progressive drive ratio transitions are made in a smooth and imperceptible manner.

A Particular object of the present invention is to pr vide a ooveldosis of fluid coup ing hav n a plurali y of unners ad pt ior c in selectively effective during operation of the cone plins whereby a loast n sp d han of h ransm ssion ca be a c mpli hed by h t n the coupl n pe ation fr m ne r nner to t ot r A still thither object of this invention is th p ov ion oi a n w ty of fl d upl nsh ing mu ip run ers whi h are s ontrolled that at e st a art f the chan e ir m one gea atio oono her is ef ected within the fluid coupling. A other o ject to p o de a mum-ran pow r transmission ha in a soared unit and a d up ing unit interconnected in which at least some of the speed changes of the transmiss-ion are ofic ted within the flu d coupling, and wherein t e control of these changes is efieoted xterna ly o the couplin This application is a division of my co-pending applicatiQIl Serial No. 237,974 filed July 21, 1951. The several objects and advantages referred to above will become more apparent upon reference to the following description taken in connection with the. accompanying drawings, in which:

Figure 1 is a vertical longitudinal section through a power transmission constructed according to my invent n d having s iated the ewith the fluid coup n unit with which the Present inventionis particula ly concerned;

Figure 2 a fr gmenta y verse s c onal Vi w, taken. on line 2+ o Figur 1 s ow n port on oi he flu d coupl ng f th s. invention; igure 3 is a more or loss di rammatic e showing the hydrau ic contr l ystem or the se cral brake bands of. the ransmiss and h mo able deflector of he d co p n o e er w h the. co trol alve f r ntro g transmis ion; and a Figure 1 i an ragmentary view showing the dofleotors oi the fluid. coup ing shi ted to a difer t operative po it on than they o cu y in igure 3- GENERAL ARRANGEMENT In general'the transmission of this invention oomcr ses thccombination of a fluid coupling having an im eller-one. two runners and a geared unit- Tho im cll nend unners are arranged so that b low a pr de ermined Speed of operation th imp llor is. coupled ith o y the i ner f the runners and above a predete ined speed the im eller v s. coupled w h th ou r oi he runners, with-the in er runne id ns- A o e n r con trolled valve is provided so that at a prdetgr 3 mined speed of operation of the engine of the vehicle, the impeller of the coupling is automatically coupled with the outer of the runners and a manual control is also provided whereby the impeller can be maintained coupled to the inner impeller at all engine speeds.

The geared unit that is provided comprises a casing having therein two or more cluster gears, each consisting of a plurality of pinions. A pair of sun gears are provided meshing with certain of the pinions, and these sun gears are connected with the runners of the fluid coupling, with the sun gear associated with the inner one of the runners being connected therewith through an overrunning clutch. 7

Another of the pinions of the cluster gears meshes with a gear on the output shaft of the transmission. Means are provided for holding the casing which mounts the cluster gears against rotation to give a driving connection between the runner driven sun gears and the output gear, and this means includes an overrunning clutch that permits rotation of the casing for obtaining a. high gear ratio.

Still another of the pinions of the cluster gears meshes with a sun gear that has an overrunning clutch between it and the impeller of the fluid coupling, so that, when this last-mentioned sun gear reaches the speed of the fluid coupling impeller, it is locked thereto and provides for an increase in the driving ratio of the transmission.

An auxiliary braking means is provided for locking the housing containing the cluster gears against rotation in either direct o hereby the transmission can be locked in low gear for coasting down hills.

Still another braking means is provided for locking one of the runner driven sun gears against rotation, whereby the transmission can be operated in reverse.

STRUCTURAL ARRANGEIVIENT The transmission according to my invention can advantageously be considered by dividing it into eight sub-assemblies, which will now be taken up in order.

1. The driving assembly The driving assembly comprises the drive shaft I8 which is provided with external multiple splines II for mating with the internal multiple splines I2 of the impeller [3 of a three-element hydraulic coupling designated by A. The impeller I3 is provided with radial vanes I4 and carries the outer member I5 of an overrunning clutch B. The drive shaft I0 is recessed to receive the outer member I8 of the overrunning clutch C and the anti-friction bearing II, which supports the output or driven shaft I8. The drive shaft I0 is also provided with passages I9 and 28 for the purpose of conducting pressure oil. The impeller I3 is also recessed for the reception of the thrust bearings 2| and 22 to keep the impeller in correct operating relationship with the other members of the coupling A.

2. The primary floating assembly The primary floating assembly consists of the runner 23 which is composed of the semi-toroidal shell 24 and the hub portion 25, into which is fitted the outer member 26 of an overrunning clutch D. Radial vane 21 connect the shell 24 and the hub 25. The inner member of the overrunning clutch D is secured to the long sleeve 28 of the driving pinion 29, which is recessed on both ends to receive anti-friction bearings 30 and 4 3|. The hub 25 is also recessed to receive the ball bearings 32 and 33 to provide for radial support and end thrust of the runner 23, respectively.

3. The secondary floating assembly The secondary floating assembly consists of the runner 34, which is composed of three sections. The left-hand section 35 conform closely to the shape of the impeller I3, and its hub 36 is journaled on the drive shaft I0 and is provided with suitable ports 31 to cooperate with the passages 28 to conduct pressure oil from the hub 38 through the oil pip 38 to the center section 39 of the runner 34. The left hand section 35 is fastened to the center section 39 by a series of screws 48. The runner 34 is provided with radial vanes 4| and an annular extension 42.

Centrally between each pair of vanes and in said annular extension cylindrical bore 43 are provided and into which closely fitted pistons 44 are inserted. Deflector shields 45 are integral with the pistons 44 and are slidably fitted between the vanes 4|, and their contour is such as to provide a smooth path to the circulating oil in the coupling. A protrusion 48 on the lefthand section of the runner 35 acts as limiting stop for the deflector shields 45 in their most xtended position, in which these deflector shields align with the contour of the semi-toroidal shell 24 and prevent any circulating oil from entering between the vanes H of the runner 34.

The third or right-hand section of the runner 34 is the recessed ring 41 which is fastened to the center section 39 by the screws 48. A series of ports 49 conduct the pressure oil which enters from the piping 38 into the recess 58, whereby said oil may readily enter the bores 43 and act on the pistons 44 therein. Likewise when the oil pressure is relieved and the centrifugal force of the circulating oil pushes on the deflector shields 45, the pistons 44 will move to the right and then permit access of the circulating oil in the coupling to the vanes 4| of the runner 34.

The center section 39 has a multiple splined hub 5| which mates with the long sleeve 52 of the pinion 53 which is recessed to receive antifriction bearings 54 and 55 which are journaled on the long sleeve 28 of the driving pinion 29. Oil seals 56 and 51 are provided to prevent oil leakage.

4. Direct drive or high ratio assembly The direct drive or high ratio assembly consists of the pinion 58 which has a long sleeve portion 59 and is recessed for the reception of anti-friction bearings 68 and 8|, which are journaled on the driven shaft I8. The inner portion of the overrunning clutch B is secured to the long sleeve 59 and cooperates with the outer portion which is secured to the impeller I3, so that the pinion 58 cannot overrun the impeller I3. The bearings 38 and 3| of the pinion 29 are alsosgournaled on the long sleeve 59 of the pinlOIl 5. The driven assembly The driven assembly consists of the long driven shaft I8, whose left-hand end is reduced to have secured to it the inner member of the overrunning clutch C which prevents the shaft I8 from overrunning the drive shaft It], also for taxipush starting of the engine by pushing the car.

To the right of pinion 58 a pinion 62 is secured to the shaft I8 and the right-hand end of 7 cated at I28, is connected for being driven as by the shaft I2I and at a predetermined speed of rotation will move valve member II8 into position to interconnect conduits I I I and I I3. Shaft I2I may be engine driven or may be driven at a speed corresponding to the speed of the vehicle, or other load being powered by the transmission.

Valve member 94 of the control valve for the bands 11, I8, and 19 has four positions into which it can selectively be adjusted manually. This is preferably done by means of a shift lever in the steering column or by any other suitable arrangement that will be convenient for the operator.

In its first position, identified by letter N," which is neutral, all of ports 95, 96, and 91 are connected with the exhaust manifold I22 that leads back to reservoir 9 I.

The next position of the valve member 94, where the member is moved to D position, and with the valves so shifted that pressure fluid is delivered to port 95 pertaining to band 11 so that the said band is energized, while the other bands I8 and 19 remain de-energized.

The transmission is now in drive ratio, and at a predetermined sped the governor valve shifts to the position illustrated in Figure 4, and this permits deflector shields 45 and their pistons 44 to move to a position where fluid will be admitted to the outer runner.

The third position for valve member 94 is marked L, and in this position both bands I1 and I8 are energized by a supply of pressure fluid to their ports 95 and 96. With th valve in this position, housing 65 of the cluster gears is locked and the transmission is forced to operate in low gear, thus providing a safety factor for coasting down long hills.

The last position that the valve member 94 can occupy is identified R, and this is the position for reverse operation of the transmission, and at that time port 91 for band I9 receives pressure fluid, while ports 95 and 95 of the other bands are connected to exhaust.

At this time the governor valve is shifted to its Figure 3 position so that only the inner runner is effective. In certain instances it might be deslrable to provide an arrangement for automatically forcing plungers 44 and deflector shields 45 outwardly whenever band I9 is energized. This could readily be accomplished by providing a pilot arrangement on the overruling valve, which would shift its valve member II to overruling position whenever port 91 of band I9 was subjected to pressure.

OPERATION Idling or neutral" position For neutral" operation of the transmission, a suitable control lever on the steering Wheel post will be set into the neutral position, whereby the control valve will be set so that all three brake bands are released, but pressure oil will be applied to the pistons 44 so that the deflector shields 45 will be held against the stops 46.

The driven shaft I8 is now stationary and with the gear ratios as stated above, and with the runner 23 and pinion 29 turning with the impeller I3. the reaction assembly will turn in the opposite direction at half the speed of the runner 23, and the runner 34 and pinion 53 will turn in the same direction at one-fourth the speed of the runner 23, and the pinion 58 also turns in the same direction, but at two-fifths the speed of the runner 23.

Forward motion in low gear To produce forward motion in low gear, the control lever is shifted into the drive position, whereby the valve is set to deliver pressure 011 to the brake cylinder which applies pressure to the free end of the brake band 'I'I to stop the reaction member from rotating backwards and cause the runners 23 and 34 to come to a stop because the output shaft I8 is still stationary, due to the application of the foot or parking brake.

Upon release of the brake and depression of the accelerator, the runner 23 will speed up, and through pinion 29, cluster gears and pinion 52 will drive the output shaft I8 at reduced speed but increased torque. As previously assumed, the pinion 29 and its mating cluster pinion have each 36 teeth, the output shaft pinion 52 has 54 teeth, and its cluster pinion mate has 18 teeth. Therefore, when the housing 55 is at rest, the shaft I8 turns at one-third the speed of the runner 23, but its torque is three times as great.

The speed of the runner 34 is now half the speed of the runner 23, and the pinion 58 turns at three-fifths the speed of the runner 23.

Forward motion in intermediate gear As the car speed increases to, say, approximately ten miles per hour. the governor will shift the valve into the position whereby the oil pressure is relieved in the pipe lines I9, 20, 38, 49, and so that the centrifugal force of the circulating oil in the coupling will push on the deflector shields 45 and force the pistons 44 to the right and permit entrance of the circulating oil into the vanes 4| of the runner 34, which will accelerate its speed and the drive will now be taken over by the pinion 53 and the runner 23 will idle along with the impeller I3, but the pinion 29 will tum faster, and this is accommodated by the overrunning clutch D.

The pinion 58 being smaller in size than 53, also rotates faster, so that when the runner 34 and pinion 53 rotate at five-sixths engine speed, the

pinion 58 will rotate at engine speed.

The speed of the output shaft I8 will then be five-ninths that of the engine, but its torque will be one and one-half times that of the input shaft I0.

Forward motion in high" gear The overrunning clutch B will prevent the pinion 58 from turning faster than the input shaft I0, so that when the pinion 53 turns at a speed in excess of five-sixths engine speed, the cluster pinion housing will be compelled to turn in the same direction as the input shaft I0, this being permitted by the overrunning clutch I2 without releasing the brake band I1, and, as a result, the output shaft speed will be increased.

As the speed of the runner 34 approaches the speed of the impeller I3, the speed of the output shaft i8 also increases. For example, if the runner 34 has two per cent slip, the speed of the output shaft I8 will be ninety-four per cent of the input shaft speed for the gear proportions stated above.

It should also be noted that the torque capacity of the hydraulic coupling must be two and twothirds times the maximum engine torque because the pinion 58 "feeds back a large portion of the circulating torque of the coupling, i. e., if the engine torque is taken as unity, then the pinion 58 feeds back one and two-thirds times enass-e946 9 gine torque to the impeller 13-, where it is added to the engine torque.

Therefore, two andtwo th-irds "engine torque is transmitted to the runnersAand pinion 53. The latter delivers through the cluster pinions unity engine torque to pin-ion 62 on the output shaft l8 and-one and two-thirds engine torque to pinion 58, which feeds it back through the-overrunning clutchBto the impeller 5' 3.

Whenthe speed-of the car is reduced due to increased torque demand, the cluster pinion 'liousing 65 will come to a halt and'its counter rotation will be prevented by the overrunning clutch l2, and the brake band '-'I 1, which is continuously applied as long as the transmission is conditioned in the drive position, and then torque multiplication again takes place.

Down-hill braking When descending steep hills, the car could attain excessive speed, "unless the brakes are applied, because there is no direct mechanical connection between the output and input shafts and the cluster pinion housing 65 cannot be held by the brake H in the'forward rotation "For these reasons the 'bra'keband T8 is provided which is capable of stopping the rotation of said housing and compelling the-transmission to operate in the low gear ratio where the engine can be effective in braking the car.

Reverse operation To produce reversefloperation of the transmission, the control lever is moved .to the reverse position. The :brake bandTI-S will :be applied, and the :brake bands :11 and :18 will be free, pressure oil being delivered :into its brake cylinder, stopping the rotation of the runner 3G and pinion 53. Pressure oil will also force the pistons 4'4 "with the deflector shields 45 to the left against thestops 46. g I

When the engine is speeded up, the runner 23 will ,be accelerated and pinion 29 .will cause the housing '65 with its cluster jpinions to planet around the :now stationary pinion 53 at the same speed, but in the opposite direction from that of the driving pinion 29. The output shaft l8 will now turn in reverse at one-third the speed of the pinion 29 and the output torque is now three times that of the input shaft.

The no-roll-back overrunning device 15 is automatically rendered ineffective because the housing 65 turns three times faster in the same direction as the output shaft l8.

From the foregoing, it will be seen that my invention provides for an automatic transmission having multiple speed ranges which makes it suitable for passenger type automotive vehicles and the like, which is of extreme simplicity, and in which all timed and overlapped shifting of clutches and brakes is eliminated.

The net result is a transmission that can be produced economically, serviced easily, and in which the changes from one speed ratio to another take place without any perceptible shock in the drive train.

It will be understood that I do not wish to be limited to the exact proportions, ratios, and other factors specifically set forth in the foregoing description and the accompanying drawings, but desire to comprehend such changes thereof as may be further desirable to adapt my invention to different conditions and usages.

I claim:

1. In a transmission of the nature described,

an input member, a pair of output members, a fluid coupling having :an impeller connected to said-input member and having first and second runners respectively connected with said output members, deflector means in said coupling for deflecting the "flu'idpumped by the "impellerinto one of said runners 01' for permitting the fluid to enter the other of the runners, fluid operated plunger means adapted for holding said deflector means in'its deflecting position, a source 0f pressure, valve means normally positioned to connect said source of pressure with said plunger means, and speed responsive means arranged for shifting said valve into position to exhaust said plunger means.

2. In a transmission of the nature described, an input member, a pair of output members, a fluid coupling having an impeller connected to saidfinputfmemberand having first and second runners respectively connected with said output members, deflector means in saidcoupli-ng for deflecting the fluid pumped by the impeller into one of said'runners or for permitting the {fluid toenter the other ofthe runners, fluid-operated plunger means adapted for holding said deflector means inits deflecting position, a source of pressure, valve means normally positioned to connect said source of pressure with said plunger means, "speed responsive means arranged for shifting said valveinto position to exhaust said plunger means, and auxiliary valve means adjustable for preventing the exhausting of said plunger means.

-3. In a hydraulic coupling; an impeller, and inner runner and an outer runner iii ,'said coupling, deflecting shield means positioned "about the outer periphery of the inner runner and movable axially *of the coupling, :said deflector means in its inner position deflecting the fluid pumped by the impeller into the inner runner and in its outer position permitting the fluid to enter the outer runner, fluid operated plunger means connected to said deflector means, and means for supplying pressure to said plunger means "to move the deflector "means to its inner position, or to exhaust I fluidlfrom said plunger means, wh'ereby'th'e pressure of thefluid pumped by the impeller will move the deflector means to its outer position.

4. In a fluid coupling; an impeller, inner and outer runners in said coupling comprising substantially concentric shell portions and blades thereon, and deflecting shield means carried by said outer runner having a first position where it extends from the exit edge of the shell of the impeller to the entrance edge of the shell of the inner runner whereby fluid pumped by the impeller enters only the inner runner, and said deflector shield means also having a second posi tion where it forms a part of the wall defined by the shell of the outer runner whereby the fluid pumped by the impeller enters the outer runner.

5. In a fluid coupling; an impeller, inner and outer runners in'said coupling comprising substantially concentric shell portions and blades thereon, and arcuate deflector shields carried by the outer runner between the blades thereof having retracted positions where they are disposed within recesses provided therefor in the shell of the outer runner and inner positions where they extend from the edge of the impeller to the edge of the inner runner to deflect the fluid from the impeller into the inner runner.

6. In a fluid coupling; an impeller, inner and outer runners in said coupling comprising substantially concentric shell portions and blades thereon, and arcuate deflector shields carried .by the outer runner between the blades thereof having retracted positions where they are disposed within recesses provided therefor in the shell of the outer runner and inner positions where they extend from the edge of the impeller to the edge of the inner runner to deflect the fluid from the impeller into the inner runner, an axial plunger extending from the back of each shield, and axial bores in the shell of the outer runner receiving said plungers.

7. In a fluid coupling; an impeller, inner and outer runners in said coupling comprising substantially concentric shell portions and blades thereon, and arcuate deflector shields carried by the outer runner between the blades thereof having retracted positions where they are disposed within recesses provided therefor in the shell of the outer runner and inner positions where they extend from the edge of the impeller to the edge of the inner runner to deflect the fluid from the impeller into th inner runner, an axial plunger extending from the back of each shield, and axial bores in the shell of the outer runner receiving said plungers, said bores being hydraulically interconnected for receiving pressure fluid to actuate said plungers in unison to move the shields to their said inner positions.

8. In a fluid coupling; an impeller, inner and outer runners in said coupling comprising substantially concentric shell portions and blades thereon, and arcuate deflector shields carried by the outer runner between the blades thereof having retracted positions where they are disposed within recesses provided therefor in the shell of the outer runner and inner positions where they extend from the edge of the impeller to the edge of the inner runner to deflect the fluid from the impeller into the inner runner, said shell of the outer runner comprising shoulder means to abut and halt said shields in their said inner positions.

9. In a fluid coupling; and impeller, innerv and outer runners in said coupling comprising substantially concentric shell portions and blades thereon, and arcuate deflector shields carried by the outer runner between the blades thereof having retracted positions where they are disposed within recesses provided therefor in the shell 01' the outer runner and inner positions where they extend from the edge of the impeller to the edge of the inner runner to deflect the fluid from the impeller into the inner runner, an axial plunger extending from the back of each shield, and axial bores in the shell of the outer runner receivin said plungers, a source of fluid pressure, and governor controlled valve means operable to connect said source to said bores below a predetermined governor speed and to connect the bores to exhaust above said predetermined speed.

10. In a fluid coupling; an impeller, inner and outer runners in said coupling comprising substantially concentric shell portions and blades thereon, and arcuate deflector shields carried by the outer runner between the'blades thereof having retracted positions where they are disposed within recesses provided therefor in the shell of the outer runner and inner positions where they extend from the edge of the impeller to the edge of the inner runner to deflect the fluid from the impeller into the inner runner, an axial plunger extending from the back of each shield, and axial bores in the shell of the outer runner receiving said plungers, a source of fluid pressure, and governor controlled valve means operable to connect said source to said bores below a predetermined governor speed and to connect the bores to exhaust above said predetermined speed, there being also a selectively operable valve for maintaining a supply of pressure to said bores independently of the operation of said governor con trolled valve means.

FREDERICK W. SEYBOLD.

References Cited in the flle of this patent UNITED STATES PATENTS Number Name Date 2,536,842 Duffield Jan. 2, 1951 2,548,272 Seybold Apr. 10, 1951 2,627,724 Seybold Feb. 10, 1953 

